Well pumping apparatus



Oct. 7, 1941. F. E. scHElDr-:R 2,258,103

WELL PUMPING `APPARATUS 5 Sheets-Sheet l Filed July 9, 1958 INVEN TOR.

FT .2.... MJ

Oct, 7, 1941. F, E, scHl-:IDER

WELL PUMPING APPARATUS Filed July 9, 1938 5 Sheets-Sheet 2 MyW/fw Oct. 7, 1941. F. E. scHl-:IDER i 2,258,103

WELL PUMP ING APPARATUS sa. [ci Jo., fr@ $5.

I NVEN TOR.

@MMM/JMW Oct 7, 191m- F. E. sci-EIDER .2,258,103

WELL PUMP ING yAPPARATUS Oct. 7, 1941. F. E. `scHE|DER WELL PUMPING APPARATUS Filed July 9, 1938 5 Sheets-Shea?I 5 INVENTOR.

Patented Oct. 7, 1941 UNITED STATES PATENT OFFICE WELL PUMPING APPARATUS Frederick Edmund Scheiden', Los Angeles, Calif. Application July 9,1938, serial No. 218,351 1o claims. ,(C'l. so-512) The present invention relates to an improved well pumping apparatus of which one embodiment includes a hydraulic engine for operating the sucker rod of a well, an accumulator for assisting in and controlling the operation of said engine, a hydraulic pump unit controlled by and which operates said engine and accumulator, and control valves and devices associated with the aforesaid elements and which together with said engine, accumulator and pump unit are constructed, interrelated and operated to provide for certain advantages and objects as will hereinafter appear.

One of the objects of this invention is to provide for the advantageous use of a comparatively long stroke of the sucker rod, for increasing the output of the well over g'iven pumping periods without entailing appreciably increased production costs.

Another object of this invention is to provide a self-contained pumping unit which may be readily and easily bodily shifted to one side of its operating position to afford full access to the well parts.

Another object is to provide a well pumping jack unit, wherein a novel form of base structure therefor is provided with an air-tight reservoir for an adequate supply of hydraulic operating fluid and includes means for cooling such fluid whereby to prevent aeration and gasing thereof and consequently prevent failure of etlicient performance of the several hydraulic units of the system.

Another object is to provide means for automatically injecting cooled fluid from a supply reservoir into the working system and likewise returning to said reservoir fromlsaid system, predetermined quantities of operating uid, during operation of the hydraulic units of the apparatus, whereby to insure the presence in the system of operating fluid inA such adequate amount and in such cooled condition as to provide for an efficient operation of the entire unit at all times.

A further object is to provide a fluid injecting means such as described which may be controlled and operated to introduce predetermined amounts of operating fluid into the system for the purpose of varying the length of the stroke of the accumulator and the hydraulic engine which actuates the sucker rod, whereby to vary the length of the stroke of the latter to best suit the particular well or conditions at hand.

A further object is to provide in the apparatus and system hereof a simple and effective means operative at and through the hydraulic pump unit thereof for varying the velocity and timing of the stroke of the sucker rod engine and associated accumulator to provide a lag during the stretching action of the sucker rod at the beginning and end of each stroke and for an accelerated stroke between such lag periods, whereby to provide for substantially the same length of stroke at the pump within the well as produced at said engine at the top of the well.

Another object is to provide a stroke velocity or timing control means of the character described which is operative through varying the volume-pressure output of the main hydraulic pump of the unit, and wherein said pump is so constructed as to readily lend itself to such variable pressure output under control of valve means in turn automatically controlled by the sucker rod engine for the purpose of controlling the movement of thesucker rod as aforesaid.

Yet another object is to provide for controlling the velocity of the sucker rod per stroke as aforesaid through the medium of stroke dampening means embodied in the accumulator and sucker rod engine, and wherein said means work in conjunction with the aforesaid valve means to jointly control the timing of the sucker rod stroke.

A further object is to provide a hydraulic sucker rod engine of the character described wherein the sucker rod load is suspended from the lower end of the plunger o'r piston thereof and provision is .made for relative adjustment of the sucker rod at the top of said engine and plunger, whereby to eliminate damaging and objectionable out of line friction producing stresses and distortion in the engine and also provide for an easier and more readily effected attachment, detachment and adjustment of the sucker rod with respect to said plunger.

Yet another object is to provide a self-contained hydraulic pumping system from all parts of which inclusive of the storage reservoir for the operating fluid, air is excluded at all times to prevent aeration of such uid and thereby insure full operating efficiency of the system.

With the above and other objects in view thel invention consists in the novel method and combination of parts hereinafter described, illustrated in the accompanying drawings, and set forth in the claims hereto appended, it being understood that various changes -in form, proportion, size and minor details of construction within the scope of the claims may be resorted to without departing from the spirit or sacrificing any advantages of the invention.

Referring to the drawings: v

Figure l is 'an elevational perspective view of the apparatus of this invention.

Figure 2 is a longitudinal view of the apparatus showing the base portion in section with directly associated parts such as the prime mover in fragmentary elevation and the pump unit as in eleva- -tion with the valve gear operating means thereof removed for clarity of illustration.

Figure 3 is a plan view of Figure 1 with the prime mover omitted for clarity of illustration of the disposition of the pump unit parts.

Figure 4 is a sectional view of the main pump unit taken on a horizontal center line plane showing the disposition of valve controlled pump iiow passages and in addition illustrating, partly 1n elevation, the control means provided for the by-pass valve.

Figure 5 is a sectional view tak'en on line 5-5 of Figure 4.

Figure 6 is a sectional view taken on line 6 6 of Figure 4.

Figure 7 is a sectional view taken on line 1-1 of Figure 5.

Figure 8 is a longitudinally sectional view of the hydraulically operated valve gear actuative of the main valves controlling the direction of liquid ow to and from the main pump unit as operative of the apparatus.

Figure 9 is a sectional view on line 9-9 of Figure 8.

Figure 10 is a vertically sectional view of the hydraulic accumulator of this invention.

Figure 11 is a sectional detail view of the valve means employed for automatically controlling the process of retention or withdrawal of operat. ing liquid otherwise injected into the hydraulic now of the apparatus.

Figure 12 is a sectional detail view of one form of relief4 valve employed.

Figure 13 is a sectional view of the governor valves controlling the operation of the hydraulically operated valve gear which in turn operates the main valves controlling and directing the main pump liquid flow.

Figure 14 is a vertically sectional view of the hydraulic engine of this invention.

Figure 15 is a head on elevational view of the hydraulic engine of the apparatus showing the position of parts complementing the main structure thereof.

Figure 16 is an enlarged detail view of the hy draulic impeller actuated by the engine plunger for relatively controlling the operationv of the main pump by-pass valve.

One form of well pumping apparatus of this invention generally comprises a base A, a hydraulic pump unit B, a prime mover C for driving said pump, a hydraulic accumulator D controlled by the pump unit and adapted to stand on the fluid column thereof for counterbalancing a certain portion of the well pumping load, and a single acting hydraulic engine E actuated by said accumulator 'and pump unit and adapted to operate a well pump. These elements and their associated parts are so constructed and arranged as to comprise a hydraulic pumping jack which will operate to raise and lower, in alternating relation, the hydraulic engine plunger (connected to the sucker rod of a well) and the accumulator (with said two units substantially counterbalancing one another) when the volumepressure flow of a iluid circulated by said pump unit is automatically directed to first one and then the other of said units in accordance with this invention.

The base A is constructed to provide for an air-tight storage and thecooling of a supply of .hydraulic iuid to be automatically injected into and automatically withdrawn from the system. It is here noted that the main liquid circulating system of the apparatus is devised to provide for the exclusion of air therefrom and that by further using a liquid from an air-tight cooled supply thereof for hydraulically operating the apparatus hereof aeration and gasing of the liquid that would otherwise occur upon long periods of use thereof is eil'ectively prevented.

In accordance with this invention a regulatable quantity of cooled liquid is constantly and automatically injected into the liquid ilow volume utilized in operating the device for the purpose of rst, cooling the said liquid volume and from which, in the case of maintaining a set length of the pumping stroke, a like volume is automatically withdrawn and returned to storage for cooling, or second, such constantly injected liquid may be utilized, at will, to build up the working liquid volume to increase the length of the pumping stroke. Reversely, by the automatically gradual withdrawal of liquid from the operating flow volume in excess of that quantity being constantly injected, the length of the pumping stroke is caused to automatically settle down to any desired set length thereof, be rendered constant upon stoppage of liquid withdrawal in excess of the injected supply and thus continue as a set pumping stroke cycle; into the requisite operating ow volume of which a constant automatically supplied cooled liquid is injected and a like quantity withdrawn.

Base A The base A as here shown includes air-tight reservoirs I and 2, Figure 2, held spaced apart by steel shapes 3. As here shown the reservoir 2 is formed of slide and bottom walls 4 and a sloping upper wall structure 5 terminating in a support 5 for accommodating the mounting of the cylinder of the hydraulic engine E whereby a vertical direct-in-line connection of the engine pistion to the sucker rod is eilected. As here shown the wall 8 of the reservoir chamber I is of truncated conical form and the horizontal upper surface thereof is of suillcient area to accommodate the mounting of the accumulator D. It is here noted that the structure forming the chamber I provides for the mounting of an injector pump unit L and a control valve M for the hydraulic pump valve gear F. The conical wall 8 is welded at its lower edge to an annular base 9 to which the bottom vI0 of chamber I is secured. A pipe coil II provides for circulation of water or other medium adapted to cool the fluid stored in the chamber or reservoir I. A circular sole plate I2 or the like is interposed between the base 9 of the chamber I and a suitable foundation (not shown) upon and to which the sole plate is secured by suitable means as the bolts I3. The sole plate I2 is further provided with the lugs I 4 adapted to engage the inner annular surface of the base I0 and maintain this end of the base structure pivotally or rotatably supported upon its foundation structure. What may be termed the well end of the base structure A rests upon an arcuate sole plate I5 or the like secured to the foundation as by means of the bolts I6. It is worthy voi' note that this structure provides a pivotal 6r turntable mounting for the device as a unit; whereby the end thereof overhanging the well may be swung or skidded aside, by suitable tackle or winch gear (not shown) attached to the base as by the clevis` I1, Figure 1, thus providing for unobstructed access to overhead gear such asv derrick equipment used in raising or lowering well structure parts.

Pump um't B The hydraulic pump unit B as here shown consists of a gear type or other suitable pump I8 disposed between the reservoirs I and 2 being held in position by the cross members I9 secured to the base members 3. 'I'his pump includes a circumferential housing 20, Figure 4, an end bell 2|, inlet port 22 and outlet port 23 of conventional form, but differs from the conventional form of such devices in having one end bell 24 provided with an automatic control valve F interconnecting the pump discharge and inlet; whereby the otherwise constant volume-pressure output of the pump is automatically modulated and applied to produce any desired working or movement cycle of the parts effecting the pumping stroke.

As valve stems and the like are packed in the usual manner to prevent leakage and the various fittings and parts of the unit are secured together by conventional bolted ilange connections, specic reference thereto is omitted except where pertinent for clarity of description.

The automatic control valve F comprises the end bell 24 having the passages 25 and 26 respectively communicating with the pump discharge and inlet, and a bore 21 intercommunicating the said passages and provided with a hollow piston 28 having the ports 29 and the dashpot piston 30 adapted to register with the dashpot 3|. In closed and open positions the ports 29 of the piston 28 register with the passage 26 to permit the escape of liquid which would otherwise be trapped in the cylinder behind the piston and prevent rapid control movement thereof. In the act of closing, the dashpot action of the piston 3|) and dashpot 3| cushion the movement of the valve and act as a limit stop therefor. It is worthy of note that this valve operates rapidly at high pressures without pounding orchattering. It is seen that the pressure of the pump discharge tends to open and that any opposed force acts to close the valve and that when such opposed force is applied as a variable or is malntained constant at any chosen degree of intensity the volume-pressure output of the pump will be either fully maintained or proportionally bypassed to the inlet side of the pump and that in consequence the work output of the pump then applied to produce a pumping stroke will correspondingly vary the action of each stroke cycle relative to dwell or pause periods at each end of the stroke and provide for acceleration, deceleration or constant velocity action of each pumping stroke cycle. Such control of the pump output is effected by means of a cam G adapted to control the setting of the valve F, and by means of cam substitution the one for another guide u. 'rms guide is provided with a stem :s which passes through a stulng box 36 and terminates in a socket 31 engaging one end of a compression spring 38 the other end of which latter engages the hollow piston 26 of the valve F. The bonnet structure of the valve F is formed to provide guideways 39, for the guide 34, and to support the operating means G' for the cam G.

each having a different cam curve, an innite 32 adapted to engage a roller 33 mounted in a75 'Ihis operating means is actuated by a hydraulic impeller G", Figures 15 and 16, controlled by the main engine E. The operating means G comprises a cylinder 40 having the pipe connections 4I and 42 and a piston 43, the' rod 44 of which latter passes through a stuiiing box 45 and is connected to a block 46. This block has an upwardly projecting pin 41 and supports a guide roller 48. A cylindrical extension 49 of the cylinder 40 surrounds the piston rod and block 46 and is provided with a longitudinal slot 50 through which the pin 41 projects, the inner surface of the cylindrical extension 49 serving as a runway and guide for the roller 48. The cylinders 4|! and 49 are provided with a grooved guideway 5| for a cam supporting shoe 52 afxed to the pin 41. The shoe 52 is provided with the abutments 53 adapted to embrace the ends of the cam member G which latter, to simplify cam exchanges, is simply laid therein-between and heldin place by the cover plate 54 secured by the bolts 55. A roller 56`is disposed to engage the cam to provide for antifrictional movement thereof.

The pump unit B also includes tri-chambered and ported fittings H and J, Figures 2 and 4, identical in form but set and connected to the pump inlet 22 and outlet 23 with similar lead and ported passages positioned in diagonally symmetrical order with relation to the longitudinal axis of the unit. Each of the said fittings is provided with cylindrical valves 51 adapted to rotate in bores 58 on the ball'bearings 59, the valve .stems 60 of each valve being provided with crank arms 6|.' As shown in Figures 2 and 3, certain passages of the fittings H and J are interconnected by crossover ducts illustrated as syphon shaped pipes, later designated. With reference to Figure 4 and considering the respective lead passages and valve ports in the order narrative of liquid ilow to and from 'the pump, and with the valves 51 set in position illustrated as governing one cycle of the two conditions of pump flow, the parts are designated as follows. In the one instance, the port 62 being closed, the continuously one directional pump discharge flows through the passage 63, crossover 54, passage 65, open port B6 and by means of closed port 61 is caused to exit at the opening 68, While simultaneously inlet of liquid to the pump will occur through the opening 69, open port 1|), passage 1|, crossover 12 and passage 'I3 to the pump inlet 22. Reversely, by simultaneously throwing the valves 51 (by means later described) Vto positions wherein port 62 is opened and ports 66 and 10 closed, it is seen that the pump discharge is eifected through port 62 to exit at opening 69 while simultaneously liquid inlet to the pump will (as port 66 is now closed) occur through the opening 68, the now open port 61 and passage 14 to the pump inlet 22. It is now seen that the volume-pressure output of the pump I8, automatically controllable by the valve F, is caused to exit at either end of the pump unit and that simultaneous inlet of uid to the pump will be also caused to occur through either end thereof in relation alternating with that of the discharge ow.

Any suitable means may be employed for actuating the valves 51 in unison and as the said ports are positioned therein at right angles to each other respectively, each valve is correspondingly rocked through a ninety degree arc in the act of alternately setting the valves. As here shown, Figure 8, a rhydraulically operated valve gear K comprises a barrel xed by brackets 16 to a plate 11, Figures 2 and 3, secured to the crossover pipe 12. 'I'he barrel 15 has capped ends 'I8 and 19 to which fluid conductors (later designated) are connected. Within the barrel 15 is mounted a floating plunger 88 the cup leathered ends thereof provided with dashpots 8| adapted to register and engage respective dashpot pistons 82 at the end of each one way plunger stroke. Slidable on the exterior of the barrel 15 is a sleeve 82' guided by a bolt 83 sliding in the slots 84 of the barrel 15 `and passing through a, hole in the plunger 88, whereby said plunger and sleeve are united for reciprocal movement which is changed to and imparted as rocking movement of the valves 51 by means of connecting rods 85 and the respective crank arms 6|. It is now seen, that upon the forceful admission and simultaneousiy free discharge of fluid from opposite ends of the barrel 15 and by alternating such admission and discharge, the said plunger ensemble will be alternately reciprocated in the said barrel and be cushioned and stopped by the said dashpot at each end of a stroke of such length as will, in combination with the radius length of. the crank arms 8|, simultaneously rock the valves 51 to alternating positions controlling the direction of the liquid flow to and from the pump I8 in the manner above described and for the purposes later set forth.

Further, the pump unit B is provided with a priming inlet 86, Figures 4 and 2, communicating with the pump inlet 22 and connected through a valved pipe 8'i to the pipe 88 which interconnects the reservoirs I and 2 for free circulation of fluid there-between. The openings 88 and 69 of the pump unit are also interconnected by the valved pipe 89 extending between openings 89' and 89 Figures 1 and 4. By this means, opening of the valve in the line 89, effects by-passing of the operating liquid from the accumulator to:

the engine and'vice versa. For example, when starting operation of the system, as when raising the accumulator as later described, a sufficient quantity of the operating fluid from the accumulator may be by-passed to the engine to raise the plunger thereof oif the bottom of the cylinder for the desired clearance of working parts. Further, the by-passing of the operating liquid effects, y as desired, relative positioning of the plungers of the accumulator and engine in op'er-l Accumulator D The accumulator D is provided for the purpose of substantially counterbalancing the weight of the well sucker rod plus one half of the well liquid aaisawa column load, and for counteracting frictional inequalities resulting from movement oi. mechanical parts of the device together with that of the iiuid fiow utilized to move these parts, and also for compensating the drag load of the sucker rod as variably characterized in each well. l

As the mechanical advantage exercised and derived from the use of the accumulator is that of standing on the well sucker rod load as counteractive thereof, it is apparent that by means of the accumulator, loaded to substantially counterbalance three fourths of the well pumping load, the power input of the device exercised in pumping the well is applied as a constant equal to substantially one fourth of the power required to otherwise directly raise the combined well sucker rod and liquid column load. To illustrate; as will appear as this description progresses, the weighted accumulator moves downward on the column of operating fluid between it and the inlet to the pump I 8 as the liquid discharge therefrom, simultaneously occurring, raises the Well sucker rod-liquid column load. Under conditions, for example, wherein liquid column and sucker rod Weights are Substantially equal per vertical foot of pumping lift, as roughly common in the art, and assuming the rod weighs one pound, the combined rod-liquid column two pounds, and the counteractive accumulator load one and one half pounds, then a one half pound differential power input is therefore required. to

raise the sucker rod. Conversely, lowering the one pound sucker rod and raising the one and one half pound accumulator requires Va one half pound differential of input effort.

As here shown the hollow plunger 95, Figures 10 and 2, of the accumulator D is secured in upright position on the top of the structure forming the chamber I, being secured thereto by the bolted flange connection 96 wherefrom a pipe 91 extends through the chamber wall 8 in sealed relation thereto and thereafter is connected to the opening 68 of the pump unit B. In the instance of this invention the plunger barrel is the moving part with the plunger stationary and consists of a barrel 98 having a flange 99 to which is secured, by bolts |88, a stuffing box |8| the skirt |82 of which extends into the barrel and is bored to provide a working fit and guideway |83 for the barrel as reciprocated on the plunger. Other- Wise, throughout their length the walls of the barrel and plunger are in spaced relation to each other for the purpose of first,'providing an annular space adapted to receive a stroke dampening or retarding device later described and second, obviate the necessity of bore nishing the barrel throughout its length to a working t on the plunger.

Resting upon the flange 99 and secured thereto by the bolts |84 a circular platform |85 provides a base upon which a plurality of weight members |86 are stacked and held in place by the rod bolts |81, Figure 2. It is here noted that the combined Weight of the members 98, |82 and |88 is such as to provide the counterbalancing operation of the device as above described.

The respective lengths of the plunger and barrel 98 being such as to provide the desired length of operating stroke, the top or head of the hollow plunger is closed as at |88 and the plunger wall provided with the ports |89. It is worthy of note that the upper end of the barrel 98 is devised to provide, with relation to the arrangement of the plunger head, a novel form of automatic stroke retarding means operative as controllingboth the beginning andending of stroke travel wherein the plunger head and upper end of the barrel are in conjunction. As illustrated the upper end of the barrel is closed by a bonnet or liner IIt) adapted to progressively encircle the plunger head providingthe annular clearance space I I I thereof which in ratio thereto decreases toward the end of the barrel and terminates in a bore I I2 slightly larger than the diameter of the plunger. In normal stroke operation, controlled as later described, the weighted barrel when standing on the fluidcolumn is stopped short of that position wherein the plunger headv would enter the bore I I2 but in abnormal conditions wherein the weighted barrel would drop; theplunger, coacting with the bore portion I2 constitutes in effect a cushioned or dashpot stoppage of the descent of the weighted barrel. In contradistinction as to the reaction of the respective parts of the bonnet with relation to movement of the plunger head, the bore IIS,

illustrated as providing a right circularrconical surface but in practice devised as a conical surface generated by a curvilinear line segment of desired contour provides a surface which together with the cylindrical exterior surface of the plunger head forms the annular space III of novel character Vconstituting an automatically efllcient means for dampening or retarding both the beginning and ending of a stroke wherein the respectiveparts are adjacent one another as described. Fbr, in the one instance as that of beginning the up stroke (with parts related as illustrated) and with a volume-pressure pump discharge (effected as described) owing through the ports |09 to actuate the up stroke, it is seen that the uid ow must first squeeze through a minimum clearance space (allotted as to area by the stroke stop relation of the barrel to that of the plunger head as more or less telescoped) before becoming effective as volume-pressure input sufficient to begin the stroke, and be followed up by progressively increased volume-pressure admission for the duration of the stroke movement wherein the parts are in telescoped relation. Conversely, during the down stroke the fluid volume utilized to produce the foregoing up stroke is expelled from the barrel under pressure, controlled in intensity by the desirable deadweight load imposed on the barrel, and occurring to be injected into the system. Anon-return check valved pipe ||1 connects the pump d ischarge to the pipe 91 and the main circulating system of the main pump unit B. .Within the bottom of the cylinder III a compression coil spring ||8 reacts to upwardly urge the lower spider formed en d of a piston rod IIS having a piston |20 thereon and which thereafter extends through a stuffing box I2| and terminates in a head |22, adapted to be engaged and depressed by the platform |05 on the accumulator barrel 98 during termination of the stroke movement of the latter. It is seen that the spring-urged up stroke of the piston |20 primes the pump with the cooled liquid from storage and that the down'stroke-.injects a quantity thereof, proportional to the piston movement, into the fluid volume operating the system wherefrom a like quantity is either removed or retained for the purposes above set forth and effected by a means later described.

' Hydraulic engine E For the purpose of directly operating the well sucker rod by the means of this invention, first,`

to automatically cushion the action of peak load stresses on the rod, secondly to provide means for suspending the rod loadv from the lowermost portion of the means connected to and serving to operate the pumping stroke thereof, thereby eliminating lateral ,load friction and strains, thirdly to provide means automatically effecting, at will, either the withdrawal or retention of surplus operating fluid injected into the system as and for the purpose specified; and lastly to provide means for automatically diminishing or increasing the sucker rod stroke, control its stroke limits and exercise variable ,control of progressive stages of sucker rodstroke movement; the hydraulic engine E here employed is constructed and operated as will now be described.

As here shown the single acting hydraulic engine E consists of the cylinder or barrel |23,

' Figures 14 and 15, secured on the top 6 of the as a return flow of fluid through the ports |09 to the inlet of the pump I8 in the manner above described. During 'termination of the down stroke of the barrel the end of the plunger first enters the largest clearance area provi-ded by the open end of the liner III! and as it progressively telescopes the plunger head, in continued descent, the clearance area I I I is variably restricted causing directly relative resistance -to expulsion of fluid from the barrel liner thereby automatically retarding termination of the down stroke of the barrel, heavily loaded to counterbalance operation of the device as above described.

Infiuz pump L As means for automatically causing an influx or injection of cooled fluid into the system for the purposes specified an injector or influx pump L is provided. As here shown a pump of thestructure forming the chamber or reservoir 2, by means of the bolted ange connection |24. By means of the bolts |25, a stuffing box |26,is

vsecured to the connection |24 and theskirt or liner |21 of this box extends into the bar'rel |23 and is bored toform with the plunger head |28 a combination of elements functioning in the same manner and for the same purpose as previously described connection with the liner ||0 and plungerhead of the accumulator D. By thus controlling the initial velocity of the up stroke movement of the sucker rod to, in this instance, cause the well mouth end thereof to dwell or pause for an appreciable and regulatable period of time allowing the well bottom end to have reached the limit of elongation occurring upon reversal of rod stroke movement; peak rodloads are proportionally diminished and the pumping stroke volume output of the well pump increased. In other words by the act of synchronizing the relative movement of the upper and lower ends of the sucker rod, unnecessary rod elongating strains are eliminated and pumping output increased inasmuch as the rod then becomes an element of more constant length whereby the Well pump stroke substantially equals the well mouth apparatus stroke.

From the .engine cylinder |23, at a point just above the rim of the liner |21, Figure 14, a pipe |29 connects with the opening 69, Figure Il, of the pump unit B. The upper end of the engine cylinder |23 is provided with a stuffing box |33, the skirt |3| of which extends into the cylinder and is bored to provide a working ilt and guideway |32 for the plunger |33. The exterior wall of plunger |33 operates, throughout the stroke length, in spaced relation tothe inner wall of the cylinder for the same purposes as hereinbefore described for the accumulator. The lower end of the hollow plunger |33 is closed by a plug member |34 providing for the polish rod stuillng box |35 and a screw threaded valve-like seat member |35. This seat is adapted to receive and support the lower end of a hollow column |31 through which the sucker or polish rod 1 extends and by and upon the top of which the l sucker rod load is borne as by set collars |38. It is here noted that by the means thus provided the sucker rod load is suspended from the lower end of the engine plunger |33; thus eliminating lateral stresses tending to cant the plunger with relation to the barrel, a feature of importance when considering the device as characterized by a pumping stroke oi' twenty feet or more. Further, the means as devised provides ready accessibility to the parts eiecting'; adjustment, removal or fastening of the sucker rod with respect to the engine plunger, for the column |31 having the guide disk or disks |39 and cap member |43 loosely engaging the plunger, may be readily withdrawn from the plunger barrel as a unit. Further, it is apparent that upon alternate admission and withdrawal of uid from the engine cylinder |23 the plunger thereof is caused to reciprocate and cause a pumping stroke movement of the well sucker rod connected thereto.

Governor Valve M stroke movements of the accumulator and engine; the governor valves M and M' are provided. As both are identical in structure and operation,

stop |55. A port |55 interconnects the ring portV |53 with the chamber |51 of the plunger barrel |5| wherein the cup leather iltted piston |58 is free to move between limits set by the ends o! thestop pin |59 (transversely iixed in the piston) extending into and respectively engaging the ends of slots |53 in the plunger |41.. With the stop pin |59 engaging 'the bottoms of the slots |53 the upper end oi' the piston |58 is ilush with the upper end of the plunger |41 and is adapted, as by the threaded bore I5|, to mount a push rod |52 in turn adapted, as by use of the collar |53, to simultaneously engage and depress the plungers and piston. In operation of the valve the conduit port |45 serves as an outlet and inlet for the fluid ow and with the parts in the relative position illustrated the port |45 and the now open by-pass port |45 accommodate a return flow to discharge through said ports as the iluid inlet port |44 is closed. With reference to the preceding up stroke oi' the plunger ena description of the one will serve for the other. l

As here shown the governor valve M comprises a body portion |4 Figure 13, having the centrally located bore |42 provided with the stulng box |43. Conduit connecting ports |44 and |45 communicate with the central bore |42, the

former serving as an inlet and the latter as an outlet and inlet to the central bore |42. A port |45 serves port |45 inlby-passing or closed relation as will appear. Slidable in the bore |42,

a plunger |41 provides a lower portion |48 for controlling the ports 44 and 45. A neck portion |48 provides an annular space or ring port |53 which in one position of the plunger (see Figure 13) serves as an open passageway in the port |45 and which, upon downward movement of the plunger whereby to align the said space with the ports |44 and |45 serves as an intervcommunicating passageway between them.

Above the neck |49 the plunger |41 is extended as a hollow cylinder portion |5| passing through and extending beyond the stuiling box gland |52 a sufllcient distance to accommodate asuitably resilient compression coil spring |53. This spring is interposed between the stumng box bland and the collared end |54 and urges the plunger upwardly an extent as permitted by the semble, iluid pressure in the chamber |51 has forced the piston |58 upward until the stop pin engages the upper end of the slots 53 whereupon relative movement of the piston in the plunger barrel ceases and both are held against further upward movement, urged by the spring |53, by the stop-collar |55 on the bottom of the plunger. It is now seen that initial downward movement o! the push'rod |52, iirst lowers the piston to the position illustrated as that o! contact of the push rod collar |53 with the now ilush top ends of the piston and plunger and with the stop pin |58 at the lower ends of the slots |53. As continued descent oi the rodpiston-plunger ensemble occurs, the full size portion of the plunger just above the port |45 supplants the ring port |53 thereby closing port |45. Upon continued travel whereby the conilnes of the ring port are wholly enclosed by the plunger bore v| 42 the lower limit of the ring port passes or opens relative to the upper limit of the port |44 whereupon fluid (under pressure) rushes through the now wholly enclosed ring port and communicating port |55 to the chamber |51 and by reaction between opposed ends of the "downheld piston |58 and chamber |51 snaps the plunger downward against the action of the spring |53 to the limit stop eiected by the pin |59 engaging the upper ends oi.' the slots |53. As the travel of the plunger effected by depressing the push rod occurs until such time as the ring and inlet ports registerin slightly open position and as the working length of the stop pin slots substantially equals the width of the ring port, the snap travel of the plunger aligns the inlet, ring and outlet ports whereupon a full-open ow oi iluid is attained and maintained by the valve.

It is here submitted that the valve motion described presents a novel and highly emcient means for completion oi' the otherwise deadstop movement of valve mechanism controlling and in turn operated by parts actuated by a liquid wherein such liquid moved parts, and in consequence the valve mechanism operated thereby, cease moving upon only cracking or partial opening or closing of valve parts.

With reference to Figures 10, 1 and 15, a governor valve M (above described) is mounted on the base of the accumulator D in upright position such that termination of the down stroke of the accumulator barrel 98 is eiiected by means thereon as the lug portion |54 of the platform engaging and depressing the push-rod |52 oi' the Likewise a governor valve M' is mounted in upright position on the side of the hydraulic engine E being supported on the bracket |68, Figure 15. and provided with an elongated push rod |62. The position of the vtop |61 of this push rod is such that termination of the down stroke of the engine plunger |33 is effected by means thereon as the flange |68 engaging and depressing the push rod |62 of the valve M for the purpose of reversing the stroke travel of the engine plunger as eiecting the up stroke thereof later described. A sump |68 and pipe |69' connects the discharge port |46 of the valve M' to reservoir chamber 2 whereinto the iluid ilow, controlled by the valve M' and utilized to operate the valve gear K, is discharged. l

With reference directed to Figures 4 and 1, an opening |10, on the volume-pressure discharge side of the pump unit B, is connected by the pipe |1|' having a valve |1| therein, to a relief valve N, Figure l2. From valve N, conduits |44' lead to the conduit inlet ports |44 respectively of the valves M and M'. It is now seen that upon opening of the valve |1| a volume-pressure ilow`from the pump unit B will freely occur through the conduit |1| and each of the conduits |44' to the valves M and M'. However,V an auxiliary volume-pressure fluid flow through the conduits B44 is derived, at will, from an auxiliary pump O. Referring to Figures 2 and 1, the pump O of conventional form is mounted on the prime mover C and driven thereby with any conventional form of drive means not shown. A suction pipe |12 connects the fluid supply of chamber 2 to the pump O and a pipe |13 connects the discharge therefrom to the conduit |44', Figure l, of the valves M and M. From the conduit inlet-outlet ports |5 of the valves M and M' respective conduits |45' lead to the respective ends of the cylinder 15, Figure 8, of the hydraulically operated valve gear K.

Operation Coordinated operation of the parts of the apparatus thus far described is as follows; with specific description of adjunctive means employed; such as those controlling sucker rod stroke length and variable stroke velocity, appearing in sequence descriptive of desirable utility of the device. To prepare the apparatus for operation the accumulator and engine plungers are disposed at rest in their down positions and together with the entire system are primed with the operating liquid. The valves 51 of the pump unit are manuali',r set in the position shown in Figure 4 and the piston 80 of the valve operating gear K is therefore disposed in the position shown in Figure 8. Owing to the accumulator.

and engine being in down position, the valves M and M are held by the push rods |62 in position below that shown in Figure 13, and such that the ring port |50 is in cracked communication with the ports |44. To now raise the accumulator the valve 11|, Figure 1, is opened, valve |14 in line |44' between valve N and valve M', Figure 1, is closed, and the primemover C is started. The operating liquid is now drawn snap the plunger barrel |5| downwardly to" by pump O from reservoir 2 through pipe |12 and discharged into pipe |13, conduit |44', through relief valve N, valved pipe |1|', opening |10, see Figure 4, to the discharge side of pump unit B. As port 62 is now closed, pressure is established in the cross-over pipe 64, port 68, now open, opening 88, see left end 4o1 Figure 4, and pipe 61, Figures 1, 2 and 3, and in the` iixed hollow plunger 95. It should be noted that as soon as pump O commences its operation the operating liquid is also forced through pipe line |44' towards valve M and M but does not reach valve M due to valve |14 being closed, see Figure 1. However, the liquid does enter valve M through the slightly cracked port |44 and then'enters the chamber |51 through port |58 whereupon to fully register the ring port |50 'with ports |44 and |45. At this time pressure exists in pipe line |45' which Ais in communication with the left end` of cylinder 15, Figure 8, but is ineffectual other than to hold the piston in the position in which -it was disposed in initially setting the valves 51 as aforesaid. After barrel plunger |5| has been snapped downward -pressure will build up toraise accumulator D.

This action takes place upon the initiation of the upward movement of 'the accumulator'but as the accumulator ascends and |64 tends to move away from the push rod |62 the liquid pressure in chamber |51 becomes eiectivetomove the plunger |58 upwardly to follow the accumulator, while barrel |5| remains stationary because of pressure in the chamber |51. The upward movement of |58 continues until pin |59 engages the upper ends of slots |60 when the fluid pressure ceases to be effective to move either |58 upwardly or |48 downwardly. After pin |50 engages the ends of slots |60, spring |53 will move barrel |5| 1upwardly and pressure in |51 will cause |58 to move upwardly until the ring port |50 moves completely abovel port |44. When however, the port |50 is blocked by the bore |42 the liquid pressure has no further raising effect on plunger |58, bui-the spring |53 will continue to act to further raise parts |5| and |58, as uid is trapped in chamber |51 at this time. As soon as the port |50 begins to register with port |46 the liquid in chamber |51 is relieved through |46 and |69' so that the plunger |58 will remain stationary While spring |53 continues to move barrel |5| upwardly until member |55 abuts the lower end of the member in which bore |42 is formed and pin |59 contacts the lower ends of slots |60, as seen in Figure 13. The height to which the accumulator is raised results in a corresponding stroke length of the engine upon operation of the apparatus, thus any desired length of pumping stroke required to feel out pumping conditions in the well is available, with progressive stages of stroke length increase, up to that of the maximum of the apparatus, automatically attainable as later described. 'I'his provides for any stroke variation without changing or adjusting the set of the well pump plunger with respect to the bottom of the well.

into and raises the accumulator D to the initial stroke height desired, whereupon valve 81,y is closed. Valves M and M are not effected in any manner by the operating liquid when raising the accumulator by means of the pump |8 exclusive of pump O since at this time valves |1| and |14 are both closed and the operating fluid from the pump I8 is therefore shut off from said valves. However, valve Mwill be raised solely by its spring |53 as the accumulator is raised, while valve M will, as is the case when the raising of the accumulator is effected by pump 0, remain in position such that the ring port |50 thereof is in partial registration with port |44.

I will now describe operation of the engine E by means of pump I8. With the accumulator now raised valve 81 is closed and valves |1| and |14 are opened and the pumping operation begins. For, as described, the engine E (plunger |33) being in the down stroke position, the push rod |62 thereof is depressed thereby opening the valve M to the flow of liquid from the main pump I8 through the now open valved pipes |1| and |14, valve M and conduit |45' to the respective end 19, Figure 8, of the valve gear K. Herein the volume-pressure liquid flow snaps the plunger 80 to the dashpot stroke stop position effected at the end 18 of the plunger barrel 15.

y As the accumulator (barrel 98 raised as described) is now in the up stroke position, the

push rod of valve M has been raised, actuated by the spring |53, whereby the liquid simultaneously expelled from the barrel end 18 by the plunger stroke, just actuated by valve M', is bypassed through the valve M to the reservoir l. Thus operated, the valve gear K throws the valves 51 to the alternative position described as causing the operating liquid to iiow into and discharge from the pump, effecting a down stroke of accumulator D and an up stroke of engine E. As the accumulator D descends the collar |83 on push rod |82 contacts the upper ends of barrel and plunger |58 and moves the latter downwardly until the port |50 starts to register with port |44, at which time the operating fluid enters chamber |51v through port |50 and |58 and reacting therein between plunger |58 and barrel |5| moves the latter downwardly with a snap action into position fully registering ports |44 and |50 wherefore a full flow of operating liquid will travel through port |45 and line |45 tothe left end 18 of cylinder 15 and move the piston 80 to the position shown in Fig-'ure 8. This will operate the links 85 and crank arms 6| so as to move the valves 51 to the position shown in Figure 4 whereby the pump |8 will draw liquid from the engine to effect the down stroke -thereof and force the liquid into the accumulator to effect the up stroke of the latter. Pump flow cycles, controlled as described, in alternating continuance, constitutes the pumping stroke operation of the device.

It is here noted that a secondary and independent liquid source is provided for operating the valve gear K through the valves M and M' as effected by continuous operation of the pump O, whereby liquid flow is caused in the system in the manner described as that of primarily raising the accumulator D. However in this instance the valve |1| is closed and therefore, the continuous flowfrom pump O, excepting that volume periodically utilized to operate the valve gear K (in the manner described) is by-passed to the reservoir 2 through the relief valve N, the adjustable spring urged plunger |15, Figure 12,

oi' which is set for the desired pressure of the liquid flow, which upon lifting of the plunger, escapes through the outlet port |18 and pipe |18 (Figure l) to reservoir 2 for return flow to and from the, pump O.

As described, each down stroke of the accumulator D will cause the influx pump L to inject, into the operating volume flow, an allotted volume of liquid governed in effects and disposition by the means P, for varying the length of the pumping stroke, mounted on and operated by the engine E. With reference to Figures 14 and 15, the control means P includes guides' |11 extending between and fixed to the flanged ends of the engine cylinder |23 and serving to slidably guide the crosshead |18 connected and reciprocally moved by the connecting rods |19 atfixed to the engine plunger head |68. 'I'he crosshead |18 is provided with a bore |80 freely slidable on a reach-bar |8| provided with the longitudinally adjustable clamp stop |82 and having its upper end formed to provide a hook portion |83, Figures 14 and 11, for suspending the reachrod for free movement thereof productive of engagement of the cam face |84 with the piston push pin |85 engaging a ball check |88 of the valve |81. This valve consists of the springurged ball check |86 to the checked sideof which a pipe |88 connects with the engine cylinder for discharge of liquid therefrom when unchecked and discharged through the pipe |89 to the reservoir 2.' It is worthy of note that the means provided and just above described performs a threefold function in operation of the apparatus. For by raising (from preoccupied position) and securing the stop clamp |82, the liquid injected by the influx pump L boosts successive engine strokes until the crosshead |18 engages the stop ,clamp and lifts the reach-rod 8| thereby opening valve |81 whereby the liquid, successively in jected, is successively vented from the system and the engine stroke length becomes an automatically maintained constant. Conversely, by lowering the stop clamp, early opening of the valve |81 vents more liquid than pump L injects, wherefor the engine stroke automatically settles" down to the new-set limits. Further, both instances of stroke length control envolving retention or withdrawal of liquid from the system, is followed by an automatic cycle of operations injecting cooled liquid into the main operating liquid iiow and venting therefrom an equtarill quantity for the purpose hereinbefore set for The variable pumping stroke velocity of the apparatus is attained by varying the volumepressure output of the main circulating pump I8, as controlled by the valve F which latter is controlled by cam G in turn operated by hydraulic means G actuated by the hydraulic impeller G. 'I'he impeller G" consists of the barrel |90 ailxed to the engine cylinder |23 having the conductors |9| and |92 respectively connected to the pipe connections 42 and 4|, Figure 5, of the cylinder 40 of the cam' operating means G. A piston rod |93 provided with the two-way cup leathered piston |94, passes through the stuiiing box |95, and the end thereof is afxed to the engine plunger head |68. The system being primed with operating liquid it is seen that this liquid acts and the movement of the two pistons.

It s hould be noted that the spring 38 of valve reacts as synchronizing stop the pumping operation, when the fluid pressure in the system exceeds that necessary for the ordinary operation thereof, as would occur in case of sanding-up or other overload action of the Well pump. At the start of operation of engine E the cam G is in position shown in Figure 4 due to the fact that the piston |94, Figure 16, is in its lowermost position and will have forced fluid beneath it into cylinder 40, Figure 5, through lines ISI and 62 thus shifting piston $3 and cam G to position shown in Figures 4 and 5. At this time the high point 32a at the right end of the cam is beneath the roller 33 whereby'to place the spring 38 under such tension as. to hold the valve 28 closed against the operating pressure of the pump as necessary to start the up stroke of the engine. As sfon as the engine moves on its up stroke the piston |94 moves correspondingly and forces luid through pipe lines Y IS2 and di into cylinder 50, Figure 5, whereby to shift the piston 63 and cam G to the right, proportionately to the movement of piston |94 and to such extent that the roller 33 will ride off the high point 32a of the cam into the low point 32h and thereby reduce the tension of the spring 38. This reduction of spring tension as will be apparent, will take place as soon as the engine has gotten started on itsfup stroke Vand the valve member 28 of valve F will then be subject to opening under the pressure developed by the pump, whereupon the fluid will by-pass into the intake side of the pump and the up stroke is decelerated. It must be borne in mind that the pump at all times operates to produce greater power than required for lifting the load on the engine. At the start of the engine the valve F as above explained is prevented from allowing a by-passing action due to the tension of the spring 38 holding valve F closed. However, after the start and as the cam G moves to relieve the spring tension, the valve F may open and bypass uid as aforesaid to decelerate the stroke of the engine. This deceleration is caused by a diminution of the volume fiow of operating fluid and the fact that the pumping of this lesser quantity of fluid into the engine than initially, requires a greater length of time for the pump to build up volume therein and therefore slows down the engine stroke. Having once started the engine as aforesaid and then decelerated its stroke immediately thereafter it is now desirable to continue the stroke at a faster and uniform speed and to this end the cam G is provided With a relatively long and high surface 32o which again increases the tension of spring 38 and prevents a by-passing operation of valve F such that maximum volume pressure from the pump is available for operating the engine. As the engine nears the end of its up stroke the cam G will have been advanced to the right vsufficiently to bring the second low point 32d near the leftend of the cam into contact with roller 33 whereby to again lessen the tension of spring 33 and decelerate the stroke of the engine in the same manner as previously described. At the extreme left end -of the cam G is another high point 32e for increasing the tension .of spring '38 and holding valve F closed when the accumulator is started on its up stroke.

Pressure gages Q and R are connected with the accumulator and sucker rod engine for indicating the respective working pressures thereof whereby the desired counterbalancing action of the accumulator with respecttothe engine may be determined.

I claim:

1. In well pumping apparatus, a hydraulic engine for operating the sucker rod of a well, a hydraulic accumulator including a reciprccable plunger hydraulically interconnected with said engine, a hydraulic pump unit, valve means as-` cally interconnected with said engine, a hydraulic pump unit, valve means responsive to strokes of the engine and accumulator for alternately directing the pump fiow to and from said engine and accumulator, means controlled by said engine for varying the fluid pressure flow from the pump unit during the working stroke of the engine to create lag and acceleration periods in said stroke.

' 3. In well pumping apparatus, a hydraulic engine for operating the sucker rod of a well, a hydraulic accumulator hydraulically interconnected with said engine, a hydraulic pump'unit, valve means operated by the engine and accumulator for alternately directing the pump flow to and from said engine and accumulator, means controlled by said engine for varying the fluid pressure iiow from the pump unit during the working stroke of the engine to create lag and acceleration periods in the stroke of the sucker rod, including valve means for by-passing fluid around the pump, a cam means for controlling said valve means and means controlled by the engine for operating said cam means.

4. In Well pumping apparatus, a hydraulic reciprccable engine for operating the sucker rod of a well, a hydraulic accumulator hydraulically interconnected with said engine, a hydraulic pump unit, valve means controlled by the en` gine and accumulator for alternately directing the pump flow to and from said engine and accumulator, means controlled by said engine for varying the fluid pressure ow from the pump unit during the working stroke of the engine including valve means responsive to fluid pressure of the pump for by-passing fluid around the pump, a cam means for controlling said valve means and'means controlled by the engine for operating said cam means, and means embodied in the` upper end of the accumulator and in the lower end of the engine and operative for creating lag periods.

' 5. In well pumping apparatus, a hydraulic engine including a cylinder, a plunger therein adapted to be connected with the sucker rod of a well, a hydraulic pump unit, valve means for directing a hydraulic operating fluid to and from said cylinder, valve means responsive to said fluid for varying the velocity of the stroke of said plunger and means controlled by said plunger for controlling said valve means.

6. In well pumping apparatus, a hydraulic reciprocal engine for operating the sucker rod of a well, a hydraulic reciprocal accumulator hydraulically connected with the engine, a hydraulic pump connected with said engine and accumulator, valve means for controlling the application of operating fluid from the accumulator to the eng-ine and vice versa via the pump, and separate operating devices which are responsive to the strokes of the engine and accumulator respectively for controlling said valve means.

'7. In well pumping apparatus, a hydraulic pump, a hydraulic reciprocal accumulator hydraulically connected with the pump, a hydraulic reciprocable engine adapted to have the stroke thereof reversed by the stroke of the accumulator and being hydraulically connected withV the stroke of the accumulator and being hydraulically connected with said pump, valve means 8. In Well pumping apparatus, a hydraulic pump, a .hydraulic reciprocal accumulator hydraulically connected with the pump, a hydraulic reciprocable engine adapted to have the stroke thereof reversed by the stroke of theaccumulator and being hydraulically connected with said pump, valve means associated with the pump for directing the hydraulic iluid from the pump to the accumulator and from thence through the pump into the engine and vice versa and separate operating devices for said valve means respectively operating responsive to and at ends of the strokes of the accumulator and engine for reversing the cycle of operation, and means associated with the engine and accumulator and operating responsive to a stroke of at least one of them for varying the iiuid content of the system for varying the length of the the strokes of the engine and accumulator.

9. In well pumping apparatus, a hydraulic pump, a hydraulic reciprocal accumulator hydraulically connected with the pump, a hydraulic reciprocable engine adapted to have the stroke thereof substantially counterbalanced by associated with the pump for directing the hydraulic uid from the pump to the accumulator and from thence through the pump into the engine and vice versa, a hydraulic operating device for said valve means, separate valves for controlling said device associated with said accumulator and engine and respectively operating responsive to and at ends of the strokes of at least one of them for reversing the cycle of operation, and means associated with the accumulator and engine and operating responsive to a stroke of one thereof for injecting fluid into the`system,.and Aother means associated with the engine and accumulator and operating responsive to a stroke of one thereof for ejecting iluid from the system.

10. In well pumping apparatus, a reciprocable hydraulic accumulator, a hydraulic pump connected therewith, a reciprocable hydraulic engine connected with the pump, valves associated With the pump and operable for directing Iluid from the pump into the accumulator to raise the accumulator and for directing the fluid from the accumulator through the pump to the engine forV FREDERICK EDMUND SCHEIDER. 

